Laundry machine



Aug. 26, 1941. H. D'. BROTMAN LAUNDRY MACHINE Filed March 6, 1959 5Sheets-Sheet l Aug. 26, 1941.

H. D. BROTMAN LAUNDRY MACHINE 5' Sheets-Sheet 2 Filed March 6, 1939attorneys Aug. 26, 1941.

H D. BROTMAN LAUNDRY MACHINE Filed March 6, 1959 5 Sheets-Sheef 3 1Zmventor 7/y7ayfl5ro/pcy,

By a r (mo u 1941- H. D. BROTMAN LAUNDRY MACHINE Filed March e,' 1959 5Sheets-Sheet 4 H. D. BROTMAN LAUNDRY MACHINE Filed March a, 19:59 5Sheets-Sheet 5 3rwentor Patented Aug. 26, 19.41

UNITED STATES PATENT OFFICE I r 2,253,; Appli zzzi lt 1 9 ;9?;:i :i0,013 13 (Ci. 14-1) This invention relates, in general, to laundry.machines and, in particular, to improvements in those machines havingvariable speed transmis-' sions.

One of the objects of this invention is to provide a new'and improvedvariable speed transmission for a laundry machine which is automaticallyoperable for varying the speed of said machine from one to another orits possible speeds and which is accurately timed and automaticallycontrolled'so that the speed changes occur at predetermined timeswherefor each new speed conditionprevails for a predetermined timeinterval.

Another object is to incorporate in a laundry machine employing avariable speed transmission a. new and improved shifting mechanism whichis automatically operated, controlled and timed so that said machineefllciently performs the plurality of duties expected thereof, such as,washing, rinsing and drying clothes without requiring the operator'sattention, presence or manipulation.

Another object is to provide in conjunction with a variable speedtransmission for a laundry machine a new and improved speed changingmechanism which is automatically and electrically operated .atpredetermined times to initiate speed changes in said transmission andwhich is automatically and mechanically operated for predetermined timeintervals to consummate said speed changes. I

Another object is to provide a new and im-' proved multispeed laundrymachine which'is shifted from one speed to the other by the coaction ofone set of means and which is controlled in the speed shitting by theco-action of another set of means, the co-action or said first set ofmeans being initiated by the co-action of said second set of means anddependent upon the motivating power for. said machine, but the co-actionof said second set of means being dependent iipon a motivating powerwhich is independent of said other motivating power, whereby the phasingor synchronizingof said motivating powers is unnecessary for efiicientoperation of the machine in' accordance with predetermined manners.

its speeds.

Another object is to improve the shifting mechanism for the variablespeed transmission employed in a laundry machine so that the relativelymovable members of said mechanism are.

at all times more accurately related to each other for safer and moreflicient operation than heretofore. v

Another object is to improve the variable speed transmission fora'laundry machine so as to minimize, without emciency losses, shocksnormally present upon and resulting from the shifting shown,diagrammatically, the timing mech anism together with a wiring diagramfor said two mechanisms;

Figs. 2, 3 and 4 are sections taken along the lines 2--2, 3--3-and 4 4,respectively, in Fig. 1, each, of said sections being partly broken awayto clarify the details of construction thereat;

Fig. 5 is a section taken along the lines-5-5 in Fig. 3; and a Fig. 6 isa view, partly in section and partly in elevation, of the assembledlaundry machine.

Referring first to Fig. 6, the assembled laundry machine shown thereincomprises, in general,

a main casing in having a selectively closed opening ii for providingaccess therethrough, an inner casing l2 rigidly supported by saidmainlcas ing and being .provided with a fluid inlet l3 and a drain l4,acylindrical tub lljournaled at its axis or rotation in the oppositewalls of said in ner casing and having a selectively closed open.-

ing it for alignment with said other opening to enable loading andunloading of said tub, a

- transmission, generally'indicated at 11, supp ted Another object is toimprove a multi-speed laundry machine so that its multi-functionperformance is carried out and controlled entirely automatically and instrict and accurate accordance with the timing predetermined therefor,as

well as to simplify its construction, to improve its compactness and tomaximize its efliciencies.

by said inner casing and in operative driving engagement with said tub,a housing l8 for said transmission, a motor IQ for drivingsaidtransmission through a belt 20, and a portion of a cluch shiftingcontrol mechanism, generally indlcated at 2|, for said. transmission.

Transmission housing l8 cooperates with a backing member 22 to formtherewithina closed chamber in which is supported the entiretransmission" and a substantial portion of the clutch shifting controlmechanism 2|, said housing and said member being removably sealedtogether at their abutting peripheries by means of bolts 23 which passthrough openings provided in one of said cooperants into threadedengagement with tapped openings in the other of said cooperants.

On the side of backing member 22 opposite the housing I8 there iscentrally formed a hollow boss 24 which is operable for insertion throuh an opening provided therefor in the adjacent wall of the inner casingI2 and which boss is externally threaded to receive a nut 25. Tighteningof nut 25 on boss 24 against the inner wall of casing I2 draws member22. and said casing together so as to lend rigid support to said memberand the housing I8 secured thereto, the face of ,is provided with anupper bearing-forming boss 21 and with a lower bearing-forming boss 28,the axes of bosses 21 being aligned, the axes of bosses 28 beingaligned, and these two pairs of aligned axes being parallel with eachother and with the axis of rotation of the tub I5. Member 22 is alsoformed with another boss 29, said boss being internally threaded andarranged on said member intermediate the other bosses 24 and 21 thereonin axial parallelism therewith. Member I8, on the other hand,is-provided with an opening 30, said :opening, in the assembly of thehousing members I8 and 22, being in alignment with the axis of the boss24 on member 22, and this axisbeing parallel with the axes of bosses.21, 28 and 29. To the member I8 over the opening 30 therein there isremovably secured, such as by screws 3|, a cupped cap member 32.

The shafts in the transmission I1 comprise, a drive shaft 33 supportedfor rotation in the bearings provided therefor by the bosses 28 on thehousing members I8 and 22 and extending out-- wardly from said member I8to receive thereon for rotation therewitha pulley 34. a driven shaft 35supported for rotation in suitable bearings provided therefor in the capmember 32 on housing member I8 and in the hollow boss 24 on housingmember 22 and extending outwardly from said member 22 throu h theopening pro- Vided therefor in the wall of the inner casing I2 and beinflattened at its outer end'to provide a male fit ing 36 thereat for thetub I5, a stub of a threaded engagement with the internally thread d bss 29 on the housing member 22, and

The gearing in the transmission I1 comprises.

a pair of axially spaced pinions 4| and 42 keyed times for selectivelyrotating said driven shaft at difl'erent speeds, said gears 43 and beingarranged on said driven shaft for constant meshing engagement with saidpinions 4| and 42,

shaft 31, a gear 41 freely mounted on shaft 31 and being press-fitted orotherwise secured to the gear 46 for rotation in accordance therewithabout the axis of said shaft 31, and a gear 48 keyed to the other drivenshaft 38 for rotating same and being arranged thereon in constant meshwith said gear 41 to be rotated in accordance therewith about the axisof said shaft 38. In operation, the drive shaft 33 effectuates thesimultaneous and continuous rotation of the two pinions 4| and 42 and ofeach and every one of the six gears 43, 44,45, 46, 41 and 48, saidpinions is to be seen therein that the driven shaft 35 and the gear 43which is freely mounted thereon cooperate to support one portion of theclutching mechanism for changing the speed of said shaft. This portionof said clutching mechanismcomprises, an annular spool 49 which istelescopically arranged centrally about the shaft 35 and closed at oneend by a wall 5|l'integral therewith, said wall and spool and the gear43 shaft fixedlv secured a ainst rotation by means ano er dr ven shaft38 sup orted for rotation in the hearings provided therefor by thebosses 2 on the housin members I8 and 22. The dr ve shaft. 33. whichshaft is mechanically associated with the stub shaft 31 anddriven-shafts 35 and 38 and which association will soon-be being securedagainst relative rotation therebetween by riveting said wall and geartogether. Theinternal peripheral wall of spool 49 is axially grooved, asat 5|, at a pair of diametrically opposite positions, and in thesegrooves are fitted diametrically arranged fingers 52 formed on the outerperipheries of a plurality of spaced annular plates 53, said platesbeing smooth at their inner peripheries and disposed freely about theshaft 35 and operable, as is seen, for relative rotative and axialmovements with respect to said shaft on accountof the free connectiontherebetween,

'for relative axial movement with respect to said gear and said spoolbecause of the spacing between said'plates, and for rotation with saidspool and gear In accordance therewith on account of themetal-to-metalcontacts 5|52. Alternately spaced between the plates 53,and also mounted about the shaft 35, is another plurality of annularplates 54, plates 54- being distinguishable from plates 53 in that theformer plates 54 are smooth at their outer peripheries to rotaterelatively with respect to the gear 4:, @001 4a and formed in one of apair of hubs 46 on said tub plates 53 and are notched at their innerperipheries, as at 55, for driven engagement with a splined portion 56on the shaft 35 so as to rotate with said shaft and in accordancetherewith and to move rotatively and axially relatively with respect tosaid gear, said spool and said jaw clutch elements.

plates 53. In order to minimize the friction between the plates 53 and54- when same are supposed to be separated during inoperation of theserve as a resilient means for opposing the contact between said plateand the plates 54 on opposite sides thereof.

The portion of the clutching mechanism which is also carried on shaft'35 and which selectively efiectuates or ineffectuates the operation ofthe plates 53 and 54 comprises, as is particularly shown in Figs. 1 and3, an annular clutch member 58 which is arranged on and aboutsaid shaftin splined engagement with the splined portion 58 thereof for rotationwith said shaft and relative axial movement therealong toward and-awayfrom the end plate of the multi-plate clutching device just described.At a substantially central portion of the member 58 there is formed acircumferential groove 58 through the agency of which said member isaxially driven, and on the end ofsaid member adjacent the multiplatedevice there is integrally formed an annular flange 88 which abuts theadjacent end plate 53 of said device to compress the plates 53 and 54thereof during operation of the clutch and which is separated therefromduring inoperation of the clutch. The opposite end of member 58 isintegrally formed with a plurality of annularly spaced, axially directedja -clutch elements 8|, and integrally formed on the periphery'ofmember58, intermediate the groove 58 and elements 8| thereof, is an annularshoulder 82 which serves as a backing means for a spring 83telescopically arranged about the member 58'against and ahead of theshoulder 82. In view of the fact that there is relative rotation betweenthe members which abut th opposite ends of the spring 83,

it is preferable to provide that end of saidsprin which otherwise restsin direct contact with and against the shoulder 82.with abearing-equipped cage member 54. It is seen in Fig. 1 that the spring 83constrains the member 58 toward the multi-plate device, which means thatthe Jawclutch elements 8| are normally out of engagement with theirpresently to be described mating Since the purpose of the clutch whichcomprises the multi-plate device and the member 58 is to drive eachtogether when desired, and since the plate which is engaged by themember 58 is the end plate 53 which splined to the shaft for rotationtherewith, the clutch member 88 is carried exclusively by the gear 44,whichis freely mounted on said shaft, and is rotated only when said gearis rotated. As is shown in Figs. 1, 2 and 3, the means for holding theclutch member 88 and the gear 44 together constitute a series ofannularly spaced pins 81 which are tightly fixed in openings providedtherefor in said member and whichextend therefrom loosely throughopenings 88 provided therefor in said gear. It will be noted that theopenings 88 in gear 44 are larger in diameter than the pins 81 receivedtherein, such provision permitting a slight and limited relativerotation between said gear and the member 88 during the engagementbetween the clutch members 58 and 88. It will also be noted that theclutch member 88 is constantly constrained toward the gear 44 supportingit by the spring 83 which abuts it. The end of the-clutch member 88adjacent the jaw-clutch elements 8| on clutch member 58 is integrallyformed with a plurality of annularly spaced, axially directed jaw clutchelements 58 which are operable for being drivingly engaged by saidelements 8| when desired. For opposing the aforementioned relativerotation between the clutch member 88 and gear 44, each pin 81 which iscarried in said member for drivingly connecting said member and saidgear. together has connected thereto one end of one of a series ofsprings I0, the other end of each of said springs being anchored to oneof a series of annularly spaced pins ll fixedly mounted in said gear.

In view of the fact that the gear. 44 is continuously driven by thepinion 42, the rotation of gear 44 being shown for illustrative purposesas rotating in a,clockwise direction when viewed in Figs. 2 and 3 andwhen looking from'left to right in Fig. 1, and in view of the fact thatthe clutch members 58 and 88 and shaft 35 also rotate in said clockwisedirection'when said members 58 and 88 are inter-engaged, tension isplaced on the springs 10 while said'members 58 and 88 are being engagedand said springs tend to absorb the shock of said engagement as well aspermit slight rotary play between said members thereupon.

.The transmission of the laundry machine is shown in Fig. 1 as being inposition for driving the shaft 35 (and tub l5) at drying speed, that is,the faster of the two speeds capable of being employed by said machine,because of the engagement shown therein between the clutch member 58 andthe multi-plate devic 49-53 54 (to which the gear 43 is permanentlyattached). Thisfaster speed is due, of course, to the favorable relationbetween the diameters of v the pinion 4| and gear 43. While in thisposirotates normally with the gear 43 and spool 49 rather than with theshaft 35 (with which the member 58 constantly rotates), it'is preferableto provide on the plate-engaging face of member 58 a disc 85 of-highcoeflicient of friction.

tion and during the drying interval, the clutch members 58 and 86 areout of engagement, the clutch member 88 and gear are rotating togetheridly about the axis of shaft 35 because of the continuous drivingengagement between the pinion 42 and said gear 44, and the tub l5 andsaid shaft 35 are driven at substantially the same speed as that of thedrive shaft 33 because of the positive engagement between the pinion 4|and the gear '43, the positive engagement between said gear 43 and themulti-plate device 4953, the positive engagement between the plates 54of the multiplate devicean'd said shaft 35, and the compression of theplates 53 and 54 caused by said clutch member 58 which is splined tosaid shaft 35. The slower, or washing, speed of the transmission,

on the other hand, is attained in movement therebetween.

when the multi-plate clutch device 49-53-54 and the clutch member 58 areout of engagement and the clutch members 58 and 86 in engagement throughthe agency of the jaw-clutch elements 6| and 69 thereof, the means forattaining such engagement being presently described and it beingsufllcient to say at present that such engagement is opposed by thespring 63 and the shock thereupon and otherwise possible damage to saidelements being substantially absorbed andeliminated by the springs 10.This engagement between the clutch members 58 and 86 through theirelements 6| and 69 drives the shaft 35 and tub at a speed well belowthat of the speed of the shaft 33 because of the relationship betweenthe diameters of the pinion 42 and the gear 44 andthe constant drivingengagement between said pinion andgear. While in this washing position,the gear 43 and-multiplate clutch device attached thereto are rotatingidly about the axis of the shaft 35, said device and the clutch member58 are out of engagement, said member 58 is in metal-to-metal :contactwith the clutch member 68, and said shaft 35 and the tub |5 are drivenat this washing speed because of the constant engagement between thepinion 42 and the gear 44, the substantially rigid connection betweensaid gear 44 and said clutch member 88, the metal-to-metal contactbetween said member 66 and said member 58, and the splined engagementbetween said member 58 and said shaft 35.

The shifting mechanism for the clutch member 58 comprises, in part, andas shown in Figs. 1 and 3, a transverse shaft 12 which is arrangedbetween the shafts 35 and 38 and journaled or otherwise supported at itsends in the front and rear walls of the housing member I8. Shaft 12pivotally carries a pair of yokes 13 and 1-4, the upper yoke 13 being socarried by said shaft near the lower ends of its bifurcations and thelower yoke 14 being so carried bysaid shaft near the upper ends of itsbifurcations. The lower ends of the bifurcations of yoke 14 are providedwith pins or rollers 15 which fit into the circumferential groove 59 onthe clutch member 58 for axially driving the latter toward and away fromthe adjacent clutch members on the shaft 35, and the upper end of theyoke 13 is provided with a cam follower 16 through which, as will soonbe described, the two yokes 13 and 14 are oscillatably driven about theaxis of the transverse shaft 12. Yoke 14 is also provided, above thepins or rollers 15, with pins 11 which are arranged adjacent the lowerends of the bifurcations of yoke .13 and operable for reception inarcuate recesses 18 formed therein. In other Words, though the yokes 13and 14 are operable for the most part for oscillatory movement togetherabout the axis of shaft 12, theprovision of the play connection betweensaid yokes by means of the pins 11 on one andthe slots 18 on the otherpermits a slight relativity This relativity in movement between theyokes 13 and 14 is provided because of the fact that there isno playbetween the yoke 13 and the means which drives it and because of thenecessity in many instances for a slight relative rotation between thejaw-clutch elements 8| and 88 before same become positively engaged, itbeing remembered that the yoke 14 is the shifting agency for the clutchmember 58 carrying the elements 6|. A pair of relatively hard rubbercushions 19 is secured to and provided between the upper ends of the yozes 13 and 14 to oppose the relative motion therebetween and cause saidyokes to move together and still to permit said relative motion whennecessary.

It will be noted in Fig. '1 that the shaft 38 is rotated continuously byand simultaneously with the shaft 33 but at a much lower speed becauseof the small diameter of each of the driving gears 42, 45 and 41 ascompared with the large diameter of each of the respective driven gears44, 4B and 48. A portion of this shaft 38 is axially splined at itsperiphery, as at 80, and drivingly carries thereon an internally splinedannular jaw clutch member 8|. Member 8| is provided .at .its singleworking face with axially directed jaw-clutch elements 82andintermediate its ends with a circumferential groove 83, said memberbeing rotatable with a the shaft 38 and axially slidable along thesplined portion 88 thereon, said member being limited in said axialmovement in one of its two directions by the hub of gear 48. Whereas theend of shaft 38 which carries the gear 48 is journaled in the bearing 21provided therefor in the hous- 4 being held against axial movement alongsaid shaft by means of said bushing and the an-' nular shoulder formedby said spline, and said sleeve being held against rotation with saidshaft by means of a positive male and female connection 86 (see Fig. 5particularly) formed at the co-engaging ends of said bushing-and saidsleeve. Freely mounted about the sleeve 85 is an annular jaw clutchmember 81 which. is

.formed with axially directed jaw-clutch eleinents 88 engageable undercertain conditions with the elements 82 on member 8| to be driventhereby.. Between the clutch members 8| and 81 there is provided aspring 89 which is telescopically arranged about the shaft 38 and0pposes the engagement between the clutch elements 82 and 88. v

The purpose ,of providing the sleeve and insuring its non-rotation bymeans of the looking connection 88 between said sleeve and the bushing84 is so that the clutch member 81, which is freely mounted on saidsleeve, will remain substantially idle and be non-rotative duringinoperation of the clutch 8|--81. This caution is taken in view of theconstant rotation of the shaft 38, and more favorable control of thetransmission i1 is obtained .by the mounting of the clutch member 81crime stationary sleeve 85 rather than by the free mounting of themember 81 directly on the shaft 38.

It will be noted in Figs."1 and 5 that the face of clutch member 81opposite the face thereof carrying the elements 88 is provided with anannular cam formation the high portion of which being shown at .80 andthe low portion of which being shown at 8| and the camming action ofwhich portions being in the direction of the axis of shaft 88. Camportions 88 and 8| gradually merge with each other to form a continuous,annular cammingsurface the high portion 88 of which is cooperablewith-the oamfollower 16 on the yoke 18, as viewed in Fig. 1, to movesaid yoke counter-clockwise about the axis of the 2,253,842 transverseshaft 12, the yoke 14 being substan- --rotating clutch member 8| intoclutching entially simultaneously moved counter-clockwise about saidaxis to throw the clutch member 58 on the shaft 85 out of the positionat present shown in Fig. 1 into clutching engagement with the clutchmember 68. During the adjacency of the cam follower 16 and the lowportion 9| of the camming surface on member 81 the clutch member 58 ismaintained in or returned to the position thereof shown in Fig. 1through the spring pressure thereupon of spring 63.

Axial movement of the clutchmember 8| toward and away from the clutchmember 81 along the splined portion 80 of shaft 38 is effectuatedthrough the agency of an L-shaped forked member 92 which is provided atits forked'end with a pair of opposed pins 93 in driving engagement withthe groove 83 on said member 8| and which is arranged with the other endextending substantially parallel with the axis of said shaft 38, saidmember 92 being pivoted intermediate its ends to a bracket 94' formovement about the vertical axis of a pivot pin 95, said bracket 94being rigidly anchored to the inner wall of the housing member I8, asshown in Fig. 5. It will be seen, when viewed in Fig. 5, that clockwisemovement of the member 92 about the vertical axis of pin 95 causes theclutch member 8| to move along the spline 80 on shaft 38 into drivingengagement with the clutch member 81, said clockwise movement beingopposed by the spring 89 which is arranged between said clutch members8| and 81. It will likewise be seen that the member 92 is normally heldin the position shown in Fig. 5 by the spring 89, or that said member isreturned to such position automatically by said spring after theabovementioned counter-clockwise movement of said member.

The free end of the pivoted clutch shifter 92 is pivotally connected, bymeans of a. pivot pin 96, to the outer end of a plunger 91, said plungerbeing one .of the elements embodied in the control mechanism 2| Plunger-91 is reciprocably mounted in a cylindrical, non-magnetic sleeve 98,said sleeve passing outwardly through and being rigidly supported by ahollow nut 99 which is threadedly secured in a threaded opening providedtherefor in the wall of housing member I8 adjacent the pivotedconnection between said plunger and the shifter 92, as shownin Fig. 5.Freely mounted about the sleeve 98 adjacent the forward face of the nut99 is an-annular plate I00, and fixedly mounted on the inner peripheralwall of said sleeve at the other end thereof is held a stationarymagnetic core I02 in magnet in rel t o s ip'with the free end of theplunger 91. Properly arranged with respect to the core I02 is amagnetizing coil I03 having lead wires I04 and I05 which pass through anopening provided therefor in a solenoid casing I08, said casing beingoperable for housing the solenoid 91-I02-I03,-and having a fittingengagement with the plate I00, a'scrw I01 being employed forstationarily holding said easing into threaded engagement with said coreI02 which is stationarily held in place by said sleeve 98.

Though the energization of the solenoid is to be explained in detail, itis readily seen that the magnetization of the core I02 causes-theplunger 91 to be drawn inwardly along the sleeve 98 into the solenoidtoward said core, this inward movementof said plunger causing theL-shaped clutch shifter 92 to move clockwise about its pivot"- againstthe pressure of spring 88 and force the through the inter-engagement ofthe follower 16 and high cam surface 90.

Returning to the normally idle clutch member 81 on the shaft 38, asshown in Figs. 1'and3, said member has fixed thereon for rotationtherewith an annular cam I08 having formed on its periphery a pluralityof circumferentially spaced high points I09 and H0, preferably thenumber of said high points shown being two and the spacing therebetweenbeing 180. .In cooperative engagement with the cam- I08 for beingreciprocably driven thereby along a vertical axis is a cam follower III,said follower being freely received within a vertical opening providedtherefor in the upper wall of the housing member follower III and isprovided at'its free end with acontact point II8. Anchored also to andinsulated from the upper wall of housing member I8 in proximity to andinsulated from the conductor H2 is another conductor II4, said 'con- 4ductor II4 being provided at the end thereof adjacent the free end ofconductor 2 with another contact point H5. The resiliency of conductorII2' normally constrains said conductor toward theotlierconductdr II4soas to interengage the contact points 3 and H5 thereon, and thisinter-engagement occurs and exists when the cam follower II I is in itslower position, that is, when the circumferential portions of the camI08 between the high points I09 and |I0 thereon are riding on the lowerend of said follower. Upon the engagement of either of the high pointsI09 and IIII on cam I08 with the v lower end of follower III, on theother hand,

' said follower is raised against the resilient force of the conductorH2 and the contact points H3 and I I5 a.re, as a result, separated.

As will be seen in the wiring diagram shown in conjunction with Fig. 1,the spring conductor H2 is electrically connected directly to the leadwire I04 of the solenoid coil I03 by a wire II6, that theother-conductor H4 is electrically connected directly to one side of thepower source for the energization of the solenoid 91-I02-I08 by a.wireII1, and that the other side of said power source is electricallyconnectedv directly to the other lead wire I05 of said solenoid coil bya wire H8. The resulting circuit, therefore, is II8-I05-I03-I04-I |6-'II2-I I 4-I I1, and this circuit is either made or broken at the contactpoints 8 and H5 on conductors H2 and 1, this circuit is open, tlieclutch members 8| and 81 on shaft 38 are out of engagement, the frictionclutch members 49-53-54 and 58 on shaft 85 are in engagement and theshaft 85 pendently upon the switch I I8.

speed. a

To continue with the description of the above mentioned wiring diagram,there is shown a driving motor I20 connected across the power source forthe solenoid 91-I02-I03, said motor being driven independently of theopening or closing of the switch II2, I I3, I I4, I I but preferably de-Motor I20 is operable for driving in accordance therewith any one of thenumerous types of well known timing devices I2I, said device beingshown, preferably for the purpose of illustration, with two circum'ferentially spaced high points I22 and I23, the spacing between pointsI22 and I23 in a counterclockwise direction representing the timerequired by or alloted to the drying phase of the transmission I1, thatis, the phase or phases during which the transmission drives the. shaft35 at the faster of its two speeds, and the spacing between points I23and I22 in a counter-clockwise direction representing the time requiredby or alloted to the washing phase of the transmission I1, that is, thephase or phases during which the transmission drives the shaft 35 at theslower of its two speeds, such as during washing, rinsing, waterchanges, etc.

Connected across the wires H6 and 1, by 6 being cooperable at differenttimes with the high points I22 and I23 on the timer I2I to close thecircuit through said switch, and the closing of said switch on eitheroccasion being only momentarily.

It has been said that the circuit II8-I06--- I03-I04-II6-II2-II4-II1 isopen in the showing in Fig. 1 and that the shaft 35 is rotating at thefaster of its two speeds. At this same time, the clutch member 8|,isIotatinglWith the shaft 38, the clutch member 81 is non-rotativelystationary on said-shaft 38, cam follower III is in the higher of itstwo positions because of its contact with the high point I09 on cam I06,cam follower 16 and the low portion III of the cam surface on clutchmember 81 are adjacent each other, and, though the switch I26 is open,the timing device I2I is being slowly, though continuously, rotated in acounterclockwise direction by the motor I20 with its high point I22gradually approaching the position whereat the contact arm I21 of saidswitch will be impressed upwardly into contact with the arm I26 to closesaid switch. The solenoid 91-I02-I03, as shown in 1,- is not beingenergized because neither the switch I26 nor the herein referred tocircuit is closed.

When the motor I20 has driven the timer I2I- counterclockwise to such anextent that the high point I 22 on the latter engages and raises the arm121 of the switch I26, said switch is thereby V tion 30 of the camsurface on clutch member 31 I is being rotated at its faster speed, thedrying engages the .cam follower 16 and drives the yokes 13 and 14counter-clockwise about the pivot 12 to disengage the clutch members49-63-64 and 66 on shaft 35 and to engage the clutch members 66 and 66,thereby causing the shaft 35 to be driven at the slower of its twospeeds. The circuit for initiating the energization of the sole,- noid31-I02-I03, and which is closed by the closing of the switch I26, isII6-l06-I03-- I04-I I6-I24-I28-I21-I25-I I1, and this circuit is closedfor a shorter length of time than that which is required for one-halfrevolution of the clutch member 81.

Though the opening of the energy initiating circuit 1 II6-I05-l03-I04-II6-I24-I28-- I21-I26-I I1 for the solenoid 31-I02-I03 occurs, by themovement of the high point I22 on timer I2I past the contact arm I21 ofswitch I26, much earlier than the arrival of the high pointIlO on camI08 at the follower III, the energization of i said solenoid continuesuntil said high point II 0 reaches said follower because of the energycontinuing circuit II8I05I03-- I04-II6-II2-II4-II1 for said solenoidhaving been closed by the engagement of the contact points H3 and M6 onconductors H2 and H4. This means that the clutch member 8i is positivelykept in clutching engagement with the clutch member 81 by thecooperation between the solenoid plunger 31 and the shifter 92. When thehalf-revolution of clutch member 61 is completed, that is, when the highpoint IIO reaches the follower III, the above mentioned energycontinuing circuit for the solenoid will be broken at H3, H5 and thesolenoid plunger will be protracted by the action of the spring 69,thereby disengaging the clutch members 8| and 31. However, by this time,the high portion 90 of the cam. surface On member 81 will be adjacentthe .cam follower 16 and will positively hold the clutch members 66 and66 in engagement with each other until the high point I23 on timer I2Ireaches the position for engagement with the arm the clutch members 63and 66 and permitting the re-engagement between the clutch members 63a.nd 43-63-64 through the action of the spring 63, so that the shaft 36is thereupon driven at the faster of its two speeds. The high point I23on timer I2I passes beyond the switch arm I21, thereby re-opening theenergy initiating circuit for the solenoid, before the high point I06on-cam I03 reaches the follower III to reopen the energy continuingcircuit for the solenoid. Upon the arrival of the high point I03 on camI03 at follower III, the clutch member 3I is thrown out of engagementwith the clutch member 31 by the de-energizatlon of the solenoid and theaction of the spring 33. but the clutch members 43-63-34 and 63 remainin engagement with each other, notwithstandingthe then adjacency of thecam follower '13 to the low portion 3| oi the cam surface on member 31,by means of the spring 63. The shaft 36 continues to rotate at thefaster of its two speeds until the high point I22 on the timer I2Ireaches the switch arm I21, after which the shaft alternately rotates atits slower and faster speeds in the above and clearly described manners.

means for intermittently energizing said electrically operated means,means between said shaft and said actuator for limiting the rotation ofth latter to the intermittent periods of said energization, and meansoperatively connecting said actuator and said switch means.

mentioned means, switch means for intermit-- tently energizing saidelectrically operated means, and switch control means fixed to saidactuator for movementtherewith and operatively connected to said switchmeans.

2. In a laundry machine having clutch means and shifting means therefor,a rotatable actuator for intermittently shifting the shifting means,means for rotating said actuator, electrically operated means foractuating said last mentioned means, switch means for intermittentlyenergizing said electrically operated means,- switchcontrol means fixedto said actuator for movement therewith and operatively connected tosaid switch means, and time control means for controlling saidelectrically operated means.

3. In a laundry machine having clutch means and shifting means therefor,a rotatable mem her having a camming surface cooperable with theshifting means for intermittently shifting the latter, means forrotating said member, electrically operated means for actuating saidlast mentioned means, switch means for intermittently energizing saidelectrically operated means, and a second member integral with saidfirst member for movement therewith and having a camming surfaceoperatively connected to said switch means.

4. In a laundry machine having clutch means and shifting means therefor,a rotatable member having a camming surface cooperable with the shiftingmeans for intermittently shifting the 7. In a laundry machine havingclutch means biased in one direction and shifting means therefor, amechanism for actuating the shifting means and comprising, a pair ofnormally disengaged clutch members operable when engaged for beingrotated one by the other, a cam rotatable dependently upon the rotationof said driven clutch member and operable for actuating the shiftingmeans to move the clutch means in a direction opposite the 'directiontoward which same is biased, means'operable for interengaging saidclutch members, and a second cam rotatable dependently upon the rotationof said first cam for efiectuating intermittent operation of said lastmentioned means.

8. In a laundry machine. having clutch means biased in one direction andshifting means therefor, a mechanism for actuating the Shifting .meansand comprising, a pair of normally disen-' gaged clutch members operablewhen, engaged for being rotated one by the other, a cam rotatabledependently upon the rotation of said driven clutch member and operablefor actuat ing the shifting means to move the clutch means in adirection opposite the direction toward which same is biased, meansoperable for interengaging said clutch members, a control for said lastmentioned means, and a second cam rotatable dependently upon therotation of said first cam for controlling said control to effectuateintermittent operation 'of said last mentioned means.

latter, means for rotating said member, electrica11y operated means foractuating said last -mentioned means, switch means for intermittentlyenergizing said electrically operated means, a second member integralwith said first member for movement therewith and having a cammingsurface operatively connected to said switch means, and time controlmeans for controlling said electrically operated means.

5. In a laundry machine having clutch means and shifting means therefor,a rotatable actuator having a camming surface cooperable with theshifting means for intermittently shifting the latter, means forrotating said actuator, electrically operated means for actuating saidlast mentioned means, a time control in circuit with said electricallyoperated means and operable at predetermined periods for energizing saidelectrically operated means-a cam rotatable with said actuator, and asecond control operatively connected to said cam for controllingsaid'circuit to control said rotation of said actuator.

' 6. Ina laundry machine having clutch means and shifting meanstherefor, a driven shaft, a rotatable actuator carried on said shaft andhaving a camming surface cooperabl 'with the shifting means forintermittently shifting the latter, means for unitarily rotating saidshaft and said actuator, electrically operated means 9. In a laundrymjachine'having a rotatable tub-carrying shaft with a clutch mechanismassociated therewith and operable for controlling the rotative speedthereof, shifting means cooperable with the clutch mechanism and movablebetween a pair of predetermined limit positions for controlling theoperation thereof, a pair of inter-engageable though normally separatedclutch members the first of which being continuously rotatable and thesecond of which being rotatable dependent upon its engagement with saidfirst clutch member, a pair of cam means rotatable unitarily butdependent upon the rotation of said second clutch member, one of saidcam means being cooperable with said shifting means .during its rotationfor eifectuating the movement thereof from one of-said limit positionsto the other, actuating means for interengaging said clutch members, andmeans operable in accordance with the rotation of said other cam meansfor controlling said actuating means.

10. In a laundry machine having clutch means and shifting meanstherefor, an actuator having an axis of rotation and being integrallyformed with a pair of camming surfaces each of'which has a high portionand a low portion, one of said camming surfaces being cooperable withthe and de-energizationof the latter, and a follower for actuating saidlast mentioned means, switch operatively inter-engaging said switchmeans and the other of said camming" surfaces and effective latter foropening and closing said switch means.

11. In a laundrymachine having clutch means and shifting means therefor,an actuator having an axis of rotation and being integrally formed withapair of camming surfaces each of which has a high portion and a lowportion, one of said camming surfaces being cooperable with the shiftingmeans and effective by means of its high and low portions forinstituting clutch engagement and dis-engagement, electrically operatedmeans for moving said actuator about said axis, switch means in circuitwith said electrically operated means for controlling energization andde-energization of the latter, and a follower operatively inter-engagingsaid switch means and the other of said camming surfaces and effectiveby means of the high and low portions of the latter for opening andclosing said switch means, the high portion of one of said surfacesbeing so arranged with respect to the low portion of the other of saidsurfaces as to be efiective simultaneously therewith.

12. In a laundry machine having clutch means and shifting meanstherefor, an actuator having an axis of rotation and being integrallyformed with a pair of camming surfaces one of, which has a high portionand a low portion and the other of which has a pair ofhigh portions anda pair of low portions, one of said camming surfaces being cooperablewith the shifting means and effective by means of its high and lowportions for instituting clutch engagement and disengagement,electrically operated means for moving said actuator about said axis,switch means in circuit with said electrically operated means forcontrolling energization and de-energization of the latter, and afollower operatively inter-engaging said switch means and the other ofsaid camming surfaces and effective by means of the high and lowportions of the latterfor opening and closing said switch means.

13. In a laundry machine having clutch means and shifting meanstherefor, an actuator having an axis of rotation and being integrallyformed with a pair of camming surfaces one of which has a high portionand a low portion and the other of which has a pair-of high portions andY inter-engaging said switch means and the other of said cammingsurfaces and effective by means of the high and low portions of thelatter for opening and closing said switch means, said pair of highportions being so arranged with respect to the first mentioned high andlow portions as to .be individually effective simultaneously therewith.

HYMAN D. BRO'I'MAN.

